JP2002364729A - Differential gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a loss of energy by shear resistance of oil to improve fuel consumption of a motor, in a differential device having an intermitting function of drive force. SOLUTION: This differential device has an outer case 3 rotationally driven by the drive force of the motor, an inner case 5 connected with a differential mechanism 29, and a clutch 17 engaging/disengaging the cases 3, 5. In the differential device, floating members 51, 51 not engaging with any of the case 3 and side gears 37, 39 are disposed between the case 3 and the side gears 37, 39 relatively rotating in a release state of connection of the clutch 17.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a differential device provided with an intermittent driving force mechanism.

[0002]

2. Description of the Related Art A differential device having a function of interrupting a driving force is disposed on a wheel side of a four-wheel drive vehicle which is separated during two-wheel drive.

[0003] Such differential devices include those in which an intermittent mechanism (for example, a clutch mechanism) for driving force is provided on the input side of the differential mechanism, and those in which it is provided on the output side of the differential mechanism.

Japanese Unexamined Patent Publication No. 5-54574 discloses a differential device 201 (first conventional example) as shown in FIG. 2, and this differential device 201 has an intermittent drive force mechanism as an input side of a differential mechanism. It is provided in.

[0005] The differential device 201 is accommodated in a differential carrier 203, and includes an outer case 205, an inner case 207, a bevel gear type differential mechanism 209,
It is composed of a meshing clutch 211 (a driving force intermittent mechanism), a hydraulic or pneumatic actuator 213, and the like.

The meshing clutch 211 includes a clutch ring 21 movably connected to an inner case 207.
5 and the outer case 205.

The actuator 213 includes the differential carrier 20
3, the clutch ring 215 is moved via the shift fork 217, and the meshing clutch 2
11 are disengaged and disengaged.

The outer case 205 is driven to rotate by the driving force of the engine input through the drive pinion gear 219 and the ring gear 221.

When the meshing clutch 211 is meshed, the rotation of the outer case 205 is distributed from the axles 223 and 225 to the left and right wheels via the inner case 207 and the differential mechanism 209, and the vehicle is driven in a four-wheel drive state. The driving performance, escape performance, stability, etc. in such as are improved.

When the engagement of the engagement clutch 211 is released, the inner case 207 and the left and right wheels are separated from the engine side, and the vehicle is driven in a two-wheel drive state, so that energy loss due to resistance is reduced and fuel consumption of the engine is reduced. improves.

A differential device (second conventional example) in which an intermittent driving mechanism is provided on the output side of a differential mechanism is disclosed in, for example, Japanese Utility Model Laid-Open No. 59-139424.

In this differential device, a meshing clutch is arranged by dividing an axle connecting one side gear and a wheel.

[0013] While the dog clutch is engaged,
When the driving force is transmitted to the left and right wheels and the vehicle is in a four-wheel drive state, when the meshing is released, one wheel is cut off and each gear of the differential mechanism idles, thereby causing the vehicle to rotate to the other wheel. No driving force is transmitted, and the vehicle is brought into a two-wheel drive state.

[0014]

Generally, the energy loss caused by the differential device is largely due to the shearing resistance of the oil caused by the sliding rotation between the output side gear and the differential case.

In particular, the differential device 201 (first
In the case where the driving force is intermittent between the outer case and the inner case as in the conventional example, while the driving force is cut off (during the two-wheel drive traveling), the outer case is switched by the 2-4 switching mechanism. While the rotation of the wheels stops, the side gears rotate relative to the outer case due to the rotation of the wheels during traveling, so that oil shear resistance always occurs between them. This shear resistance causes an energy loss, which in turn affects the fuel economy of the vehicle.

Also, in the case of a differential device such as the second conventional example in which the driving force is intermittently interposed between the side gears and the wheels, while the driving force is cut off and the vehicle is driven by two wheels, the vehicle is not driven. The rotation of the wheels causes the side gears to make a differential rotation, and the shear resistance of the oil is always generated between the side gears and the differential case. Therefore, the fuel consumption is affected by energy loss.

[0017] In the differential device in which the driving force is intermittently interposed between the outer case and the inner case, the difference between the radial direction of the inner case and the outer case, and the difference between the axial direction of the inner case and the outer case, respectively. The shear rotation of the oil causes shearing resistance of the oil, and the fuel consumption is affected by energy loss.

Furthermore, in any of the differential devices, if the vehicle turns and travels or travels on an uneven road during four-wheel drive travel, the side gears rotate differentially, causing oil shear resistance.

It is said that the sum of the resistances generated at these three points accounts for about 80% of the resistance generated in the entire differential device.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a differential device that has a function of intermittently driving a driving force, greatly reduces energy loss due to oil shear resistance, and can improve fuel efficiency.

[0021]

According to a first aspect of the present invention, there is provided a differential device comprising: a differential case which is rotationally driven by a driving force of a motor; a differential mechanism which distributes rotation of the differential case from a pair of output side gears to wheels; And a floating member that does not engage with any of these components is disposed between the differential case and the member that rotates relative to the differential case when the driving force is cut off by the interrupting portion. And

In a four-wheel drive vehicle, this differential device is disposed on a wheel side that is disconnected during two-wheel drive, and when an on-off mechanism (clutch) is connected, torque (driving force) is sent to the wheel side to cause the vehicle to rotate. Becomes a four-wheel drive state, and when the clutch is disengaged, the driving force to the wheel side is cut off, and the vehicle enters a two-wheel drive state.

In the differential device of the present invention, the number of sliding surfaces between the differential case and the relative rotation member is increased by disposing the floating member between the differential case and the member that rotates relative to the differential case.

For example, if one floating member is arranged, the number of sliding surfaces is doubled. If two floating members are arranged, the number of sliding surfaces is tripled. The sliding speed on the moving surface decreases.

Further, the shear resistance of the oil generated on the sliding surface is not proportional to the sliding speed, but increases sharply as the sliding speed increases.

Therefore, the effect of reducing the shear resistance by reducing the sliding speed on the sliding surface greatly exceeds the effect of increasing the shear resistance by increasing the number of sliding surfaces. Is greatly reduced by increasing.

By arranging the floating members at the above three locations, energy loss of the prime mover can be reduced, and fuel efficiency can be greatly improved.

According to a second aspect of the present invention, in the differential device according to the first aspect, the relative rotation member with respect to the differential case is a side gear, and one or more floating members are arranged between the differential case and the side gear. Thus, the same operation and effect as those of the first aspect can be obtained.

In a differential device in which a driving force is intermittently interposed between an outer case and an inner case, and a side gear and an outer case rotate relative to each other by rotation of wheels during two-wheel drive of the vehicle, a differential case is provided. By arranging the floating member between the side gear and the side gear, the shear resistance of the oil is particularly effectively reduced, the energy loss is reduced, and the fuel efficiency is greatly improved.

Further, in the case of a differential device in which the driving force is intermittently interposed between the side gears and the wheels and the side gears are differentially rotated by the rotation of the wheels during the two-wheel drive running of the vehicle, the differential case and the side gears are also used. By arranging the floating member between them, the shear resistance of the oil is particularly effectively reduced, the energy loss is reduced, and the fuel efficiency is greatly improved.

Also, in any of the differential devices, when the vehicle turns while driving with four wheels, the shearing resistance of the oil due to the differential rotation of the side gear when traveling on an uneven road is reduced, and the energy loss is reduced. , Improve fuel economy.

A third aspect of the present invention is the differential device according to the first or second aspect, further comprising an inner case rotatable relative to the differential case, and connecting a differential mechanism to the inner case. The intermittent driving force mechanism is disposed between the differential case and the inner case, and the same operation and effect as those of the first or second aspect can be obtained.

This configuration is a differential device for intermittently driving force between a differential case (outer case) and an inner case (the input side of a differential mechanism).

Further, in this configuration, as described in claim 2, if a floating member is arranged between the outer case and the side gear, the shear resistance of the oil is effectively reduced, and the energy loss is reduced. Fuel efficiency is greatly improved.

Further, if a floating member is arranged between the outer case and the inner case which rotate relatively during the two-wheel drive running of the vehicle, the shear resistance of the oil is effectively reduced, and the energy loss is reduced. , Fuel efficiency is greatly improved.

According to a fourth aspect of the present invention, there is provided the differential device according to the first or second aspect, wherein the intermittent driving force mechanism is disposed between any one of the side gears and the wheel thereof. As a feature, the same operation and effect as the configuration of claim 1 or 2 can be obtained.

This configuration is a differential device for interrupting the driving force between the side gear and the wheel (the output side of the differential mechanism). Generally, the interrupting of the driving force is performed on the axle connecting the side gear and the wheel. By doing so, A. D.
It is called D (axle disconnect differential).

In this configuration, as described in claim 2, if a floating member is disposed between the side gear that differentially rotates during the two-wheel drive running of the vehicle and the differential case, the shear resistance of the oil is reduced. Energy consumption is reduced, and fuel efficiency is greatly improved.

[0039]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A front differential 1 (one embodiment) will be described with reference to FIG.

The front differential 1 has the features of the first, second and third aspects. FIG. 1 shows the front differential 1, and the left and right directions are the four-wheel drive vehicle using the front differential 1 and the left and right directions in FIG. In the following description, members and the like not given reference numerals are not shown.

The front differential 1 (a differential device for distributing the driving force of the engine to the left and right front wheels) is a differential device having an intermittent function of the driving force on the input side of the differential mechanism, and is used in a four-wheel drive vehicle. When driving two wheels, the driving force to the front wheels is cut off.

A power transmission system of a four-wheel drive vehicle using the front differential 1 includes an engine (motor), a transmission, a transfer, a 2-4 switching mechanism, a propeller shaft on the front wheel side, a front differential 1, a front axle, left and right front wheel,
It is composed of a propeller shaft on the rear wheel side, a rear differential (a differential device for distributing the driving force of the engine to the left and right rear wheels), a rear axle, left and right rear wheels, and the like.

The 2-4 switching mechanism constitutes a front wheel side output interface of the transfer. As described below, the connection release operation and the connection operation are performed in conjunction with the front differential 1 to intermittently drive the front wheel side. I do.

The driving force of the engine is transmitted from the transmission to the transfer, and is distributed from the transfer to the front wheels and the rear wheels.

The driving force distributed to the rear wheels is transmitted from the rear wheel propeller shaft to the rear differential, and is distributed from the rear differentials to the left and right rear wheels via the rear axle.

The driving force distributed to the front wheels is 2−2 while the 2-4 switching mechanism and the front differential 1 are connected.
The four switching mechanisms, the front-wheel-side propeller shaft, and the front differential 1 are distributed to the left and right front wheels via the front axle, and the vehicle enters a four-wheel drive state.

When the connection between the 2-4 switching mechanism and the front differential 1 is released, the front wheels are disconnected from the engine, and the vehicle enters a two-wheel drive state.

The front differential 1 is arranged inside a differential carrier, and an oil reservoir is formed inside the differential carrier.

The front differential 1 has a double casing structure composed of an outer case 3 (diff case) and an inner case 5, and the inner case 5 is
It is rotatably arranged inside. The left and right boss portions 7, 9 formed on the outer case 3 are supported by a differential carrier via bearings.

A ring gear is fixed to the outer case 3 with bolts. The ring gear meshes with a drive pinion gear, and the drive pinion gear is formed integrally with the drive pinion shaft. The drive pinion shaft is connected to a transfer 2-4 switching mechanism via a joint and a front wheel side propeller shaft, etc.
The outer case 3 is rotated from the switching mechanism 4 via the front-wheel-side power transmission system.

A clutch ring 11 is disposed inside the outer case 3 and is supported on the inner periphery of the outer case 3 so as to be movable in the axial direction.

A ring 14 having meshing teeth 13 is welded to the right end of the inner case 5.
Mesh teeth 15 are formed on the clutch ring 11. These meshing teeth 13 and 15 constitute a dog clutch 17 (intermittent driving force mechanism).

Openings 19 and 21 through which oil flows in and out are provided at the right and left sides of the outer case 3 at regular intervals in the circumferential direction. In addition, four legs 23 are provided at the right end of the clutch ring 11 at equal intervals in the circumferential direction, and these legs 23 are engaged with the right opening 21 and protrude to the outside.

The clutch ring 11 is moved left and right as described below. When the clutch ring 11 is moved to the left, the dog clutch 17 is engaged to connect the outer case 3 and the inner case 5, and when the clutch ring 11 returns to the right, the engagement of the dog clutch 17 is released, Outer case 3 and inner case 5
And is separated.

A gap 25 is provided between the left end of the inner case 5 and the outer case 3. This gap 2
Reference numeral 5 denotes an oil flow path, which supplies sufficient oil to a gap 26 between the outer case 3 and the inner case 5.

The inner case 5 has a plurality of through holes 27.
Are provided at equal intervals in the circumferential direction.
Each pinion shaft 3 of the bevel gear type differential mechanism 29
Numerals 1 engage the respective tips and are prevented from coming off by spring pins 33.

A pinion gear 35 is rotatably supported on each pinion shaft 31.
The left and right side gears 5 and 5 are engaged with output side gears 37 and 39 (relative rotating members with respect to the differential case).

The bosses 41, 4 of the side gears 37, 39
Reference numeral 3 is supported by support portions 45 and 46 formed on the outer case 3, and left and right front axles are spline-connected to the boss portions 41 and 43, respectively.

Each of the side gears 37 and 39 supports the inner case 5 by a supporting portion 47 and 49 respectively formed. The inner case 5 is thus supported by the side gears 37 and 39 (the supporting portions 47 and 49). ) Are positioned in the radial direction and the axial direction.

Two floating rings 51 are provided between each of the side gears 37 and 39 and the outer case 3.
(Floating member) is arranged, and the side gear 37,
39 engagement thrust forces.

The floating ring 51 has an inner diameter slightly larger than that of the bosses 41 and 43, and is arranged in a floating state with respect to both the outer case 3 and the side gears 37 and 39.

Further, each floating ring 51
Abrasion resistance is improved by the nitriding treatment applied to the surface, and oil retention and lubrication are improved by fine irregularities formed by the nitriding treatment.

A spherical washer 53 is formed on the inner periphery of the inner case 5 so as to face each of the pinion gears 35. The centrifugal force of the pinion gear 35 and the side gears 37 and
The engagement with the pinion 39 bears the engagement reaction force that the pinion gear 35 receives.

A ring-shaped pneumatic actuator 55 is disposed around the right boss 9 of the outer case 3 and is supported by a differential carrier via a support member 57.
It is stopped.

In this actuator 55, a pressure chamber 63 is formed by hermetically fixing a diaphragm 61 to a substrate 59, and a pressing member 65 is fixed to the diaphragm 61.

The actuator 55 (the pressing member 6)
A retainer 67 is arranged between 5) and the clutch ring 11.

The retainer 67 is provided with radial locking arms 69 at positions corresponding to the four legs 23 of the clutch ring 11, and each locking arm 69 has an axial locking arm 71.
Are formed. The retainer 67 is connected to the clutch ring 11 so as to be integrally movable by sandwiching the leg 23 between the locking arm 69 and the locking arm 71.

Further, on the outer periphery of the retainer 67, four spring portions 73 are formed at equal intervals in the circumferential direction. These spring portions 73 are in contact with the right end surface of the outer case 3 and urge the clutch ring 11 in the direction in which the dog clutch 17 is disengaged (to the right).

The pressure chamber 63 of the actuator 55 is connected to a compressor mounted on the vehicle via an air pipe 75. When air pressure is sent to the pressure chamber 63, the diaphragm 61
Is displaced to the left, the clutch ring 11 is moved to the left via the pressing member 65 and the retainer 67 while bending each spring portion 73 of the retainer 67, and the dog clutch 17 is engaged.

When the supply of air pressure to the pressure chamber 63 is stopped, the biasing force of each spring portion 73 causes the clutch ring 1
1 returns to the right, and the engagement of the dog clutch 17 is released.

As described above, the 2-4 switching mechanism and the intermittent function (the dog clutch 17) of the front differential 1 are simultaneously operated when switching from the two-wheel drive state to the four-wheel drive state, and the four-wheel drive state is switched. At the time of switching to the two-wheel drive state, the connection release operation is performed at the same time.

In the four-wheel drive state, the driving force of the engine is 2
-4 is transmitted from the switching mechanism to the outer case 3 via the front wheel side power transmission system, and the inner case 5 is rotationally driven via the dog clutch 17. This rotation is distributed from the pinion shaft 31 to the side gears 37 and 39 via the pinion gear 35, and transmitted to the left and right front wheels via the respective axles.

Further, for example, when a driving resistance difference is generated between the front wheels during running on a rough road and one of the left and right front wheels idles, the driving force of the engine is differentially transmitted to the left and right front wheels with the rotation of each pinion gear 35. Distributed.

In the two-wheel drive state, the dog clutch 17 causes the inner case 5 to the front wheels to rotate freely, and the power transmission system from the 2-4 switching mechanism to the outer case 3 uses the driving force of the engine and the front wheels. It is separated from both entourage and rotation stops.

As described above, in the two-wheel drive state, the rotation of the front wheel side power transmission system is stopped, so that the vibration is reduced and the riding comfort is improved, and the wear of each part of the front wheel side power transmission system is reduced. The durability is improved, and further, the loss of energy is suppressed by the reduced rotational resistance, the load on the engine is reduced, and the fuel efficiency is improved.

In the outer case 3, spiral oil grooves 77, 79 are formed on the inner periphery of the bosses 7, 9, respectively, in addition to the openings 19, 21. Oil grooves 77 and 7
Oil grooves 81 and 83 are formed, each of which is in communication with the corresponding oil groove 9.

The openings 19 and 21 are formed in a radially outer portion on the outer case 3 and are immersed in oil in an oil reservoir formed in the differential carrier, so that the oil always flows out as the outer case 3 rotates. Enter.

The oil in the oil sump is scraped up by the rotation of the outer case 3 (ring gear), and the scraped-up oil is actuated by the oil pumps of the oil grooves 77, 79 and the oil grooves 81, 83, the floating ring 51, and the floating ring 51. The air flows into the outer case 3 through a gap such as 51.

The oil that has flowed into the outer case 3 in this manner is supplied to the respective gears 35, 3 constituting the differential mechanism 29.
7, 39, a sliding portion between the pinion shaft 31 and the pinion gear 35, a sliding portion between the outer case 3, the floating rings 51, 51 and the side gears 37, 39, and a sliding portion between the outer case 3 and the clutch ring 11. ,
It is supplied to a dog clutch 17 (mesh teeth 13, 15) and the like to lubricate and cool them.

The actuator 55 (the pressing member 6)
The lower part of 5) is also immersed in the oil of the oil reservoir, and the sliding part between the retainer 67 and the pressing member 65 is also sufficiently lubricated and cooled, wear is prevented, and the durability is kept high.

Further, in each of the above-mentioned sliding portions, wear is reduced by lubrication and cooling effects of oil, durability is improved, frictional resistance is reduced, energy loss is suppressed, and fuel consumption of the engine is accordingly reduced. Has improved.

In particular, the outer case 3 and each side gear 3
7 and 39, the two floating rings 51 are arranged so that the number of sliding surfaces between the outer case 3 and each of the side gears 37 and 39 is reduced from one to three (the outer case 3 and the floating ring 51). And sliding surfaces between the floating ring 51 and the side gears 37, 39)
Has increased.

In each sliding surface, the sliding speed is reduced by the increase in the number of sliding surfaces. As described above, the effect of reducing the shearing resistance by reducing the sliding speed in each sliding surface is as follows. Since the effect of increasing the shear resistance due to the increase in the number of moving surfaces is greatly exceeded, the shear resistance of the oil is greatly reduced, the energy loss due to the shear resistance is suppressed, and the fuel efficiency is further improved.

Thus, the front differential 1 is configured.

As described above, in the front differential 1, the number of sliding surfaces between the side gears 37, 39 and the outer case 3 is tripled by disposing the floating rings 51, 51 between them. In addition, the shear resistance of the oil is reduced, thereby reducing the energy loss, thereby greatly improving the fuel economy of the engine.

During the two-wheel drive running of the vehicle, the side gears 37 and 39 and the outer case 3 are rotated by the front wheels.
Are constantly rotated relative to each other, so that the effect of arranging the floating rings 51 and 51 between them has a particularly great effect of reducing the oil shear resistance, reducing the energy loss, and improving the fuel efficiency.

Further, the space between each of the side gears 37 and 39 and the outer case 3 (oil grooves 81 and 83) is an oil flow path.
By arranging 51, the effect of reducing the shear resistance of oil and the effect of reducing energy loss are improved, and the fuel efficiency is further improved.

In the present invention, the location of the floating member is not limited to between the side gear and the differential case (outer case).

For example, in the differential device according to the third aspect, in which the driving force is intermittent between the outer case and the inner case, between the radial direction of the inner case and the outer case, or between the axial direction of the inner case and the outer case. A floating member may be arranged between them.

Further, in the present invention, in order to make the floating member float, in addition to arranging the floating member so as not to be engaged with the relative rotation member (for example, providing an appropriate gap), the embodiment As described above, it is effective to form minute irregularities on the floating ring 51 by the nitriding treatment to enhance the oil retaining property and prevent the floating member and the relative rotation member from rotating together.

Further, the method of providing minute irregularities on the floating member is not limited to nitriding.

Further, if one floating member is arranged, the number of sliding surfaces between the relative rotating members becomes two, and if two floating members are arranged, the number of sliding surfaces becomes three, and the shearing resistance of the oil is reduced. Although the number of floating members can be reduced accordingly, the number of arranged floating members may be selected in accordance with a desired effect of reducing shear resistance and a margin of space at an arrangement location.

Further, according to the structure of claim 4, as described above,
A differential device for intermittently driving power between a side gear and wheels (an output side of a differential mechanism). A floating member is provided between a side gear and a differential case, which are always differentially rotating during two-wheel drive of a vehicle. By arranging, the shear resistance of the oil is effectively reduced, the loss of energy is suppressed, and the fuel efficiency is greatly improved.

Further, according to the fourth aspect, there is provided the differential apparatus according to the fourth aspect. D. D (axle disconnect differential)
The driving force intermittent mechanism may be arranged outside or inside the differential case.

Further, in the present invention, the intermittent mechanism of the driving force may be not only the meshing clutch but also a friction clutch such as a multi-plate clutch or a cone clutch.

Further, the actuator of the clutch may be a hydraulic actuator in addition to the pneumatic actuator, and is not limited to such a fluid pressure actuator.
For example, an actuator using an electric motor or an electromagnetic actuator may be used.

In the present invention, the differential mechanism is not limited to a bevel gear type differential mechanism, but may be a planetary gear type differential mechanism.

Further, the differential device of the present invention
In a four-wheel drive vehicle, it can be used not only for a front differential but also for a rear differential.

Further, in a four-wheel drive vehicle equipped with a winch,
The differential device of the present invention can be used for a center differential (a differential device for distributing the driving force of a prime mover to front wheels and rear wheels). If the driving force is cut off by the center differential, a winch can be used.

[0100]

According to the differential apparatus of the present invention, the floating member disposed between the differential case and the relative rotating member reduces the oil shear resistance, thereby suppressing the energy loss and consequently the fuel efficiency of the prime mover. Significantly improved.

According to the differential device of the second aspect, the same effect as the configuration of the first aspect can be obtained.

Further, the differential device for interrupting the driving force between the outer case and the inner case and the differential device for interrupting the driving force between the side gears and the wheels particularly effectively reduce the shear resistance of the oil. Energy loss is reduced and fuel economy is greatly improved.

The differential device according to the third aspect can obtain the same effect as the configuration according to the first or second aspect.

Further, by arranging a floating member between the outer case and the side gear, or between the outer case and the inner case, which rotates relatively during two-wheel drive running of the vehicle, the shear resistance of the oil is effectively reduced. , Energy loss is reduced and fuel economy is greatly improved.

According to the differential device of the fourth aspect, the same effect as the configuration of the first or second aspect can be obtained.

Further, by disposing the floating member between the side gear that differentially rotates during the two-wheel drive running of the vehicle and the differential case, the shear resistance of oil is effectively reduced, and the loss of energy is suppressed. Fuel efficiency is greatly improved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of one embodiment.

FIG. 2 is a sectional view of a conventional example.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Front differential (differential device) 3 Outer case (differential case) 5 Inner case 17 Dog clutch (intermittent mechanism of driving force) 29 Differential mechanism 37, 39 Output side gear (rotary member relative to differential case) 51 Floating ring (floating member)

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3D036 GA14 GA38 GB05 GD04 GF03 GH08 GH26 GJ17 3J027 FA07 FA50 FB04 HA01 HA03 HC10 HC29 HG07 HH20

Claims (4)

[Claims] A differential case that is rotated by a driving force of a prime mover, a differential mechanism that distributes rotation of the differential case from a pair of output side gears to a wheel side, and a driving force intermittent mechanism. A differential device, wherein a floating member that does not engage with any of the differential case and the member that rotates relative to the differential case when the driving force is cut off is disposed. 2. The invention according to claim 1, wherein the relative rotation member with respect to the differential case is a side gear,
A differential device comprising one or more floating members disposed between a differential case and a side gear. 3. The invention according to claim 1, further comprising an inner case rotatable relative to the differential case, wherein a differential mechanism is connected to the inner case, and a driving force intermittent mechanism is provided. Is arranged between the differential case and the inner case. 4. The differential device according to claim 1, wherein the intermittent driving force mechanism is arranged between one of the side gears and its wheel.